Water refrigeration



R. C. ROE

WATER REFRIGERATION v June 30, 1936.

Filed Feb. 25, 1933 4 Sheets-Sheet 1 fW/QNVENTOR ATTORNEY .June 30, i936.. R. c. RQE

WATER REFRIGERATION Filed Feb. 23, 1933 4 Sheets-Sheet 2 Sv ma lNVENTOR ATTORNEY Jim@ 3G, 1936. R Q ROE 2,045,999

WATER REFR IGERAT ION Filed Feb. 25, 1933 4 Sheets-Sheet 3 @W INVENTOR ATTORNEY June 30, 1936. R. c. ROE

WATER REFRIGERAT ION Filed Feb. 23, 1953 4 Sheets-Sheet 4 @l 6 @NVENTOR ATTORNEY Patented June 30, 1936 UNITED STATES PATENT OFFICE WATEB BEFBIGERATION Ralph C. Boe, Englewood, N. J.

Application February 23, 1933, Serial No. 658,106

17 Claims. (Cl. 62-115) My invention relates to improvements in water refrigeration and more particularly to improvements in water refrigeration as applied to air conditioning. Further objects of my invention are a simplification and cheapening of water refrigeration apparatus, together with lncreased reliability of such apparatus and ability to operate it from electrical sources. Further objects of my invention will become apparent as the specifications appear and proceed.

In the present state of the art, the vacuumization necessary for water refrigeration is nearly always performed by means of steam actuated vacuum pumps which are supplied with steam from boilers and other cumbersome and heavy equipment. Where this steam is not available, water refrigeration is not used.

In my invention, I am improving this art to permit a more universal use of water refrigeration, particularly in small sizes and for the cooling of small buildings, residences and homes.

In the figures, Figure 1 is a side schematic partial cross sectional drawing of my preferred method of water refrigeration as applied to air conditioning, Figure 2 is a cross sectional elevation of a portion of Figure 1 along lines 2--2, Figure 3 is a side schematic partial -cross sectional drawing of an alternate, and in'some few cases a more desirable method of utilizing water refrigeration, than in my preferred arrangement. Figure 4 is a partial cross sectional plan view of a portion of the apparatus in Figure' i, Figure 5 is a side schematic partial cross sectional drawing of an alternate method of water refrigeration which in some few cases is preferable to Figures 1 or 3. Figure 6 is a partial cross sectional view of Figure 5 along lines G--6. Figure '1 is a plan cross sectional portion of Figure 5 along lines 1 1. Figure 8 is a detail drawing of a steam actuated jet pump similar to that used in the previous figures. Figure 9 is a cross section of a portion of Figure 8 along lines 9-9. "j

In the figures, I are fans handling-jah to be cooled, 2--2 are cross sectional lines in Figure 1, 3 is a heat exchanger for cooling air with cold water, 4 is a n tube heat exchange surface in heat exchanger 3, 5 is a louver for inlet air to heat exchanger 3, B-S are cross sectional lines in Figure 5 referring to Figure 6, 1--1 are cross sectional lines in Figure 5 referring to Figure '1, 8 is an evaporator,

circulating water from evaporator 8 through heat exchanger 3 and spray I0, I3 is a motor driving pump I2, I4 is a conduit from pump I2 to heat exchanger 3, I5 is a conduit from heat exchanger 3 to evaporator 8, I6 is a valve controlling water supply to evaporator 8, I1 is a float controlling valve I6, I8 is a receiver working at approximately atmospheric pressure, I9 is a heat exchanger operated by fuel or any suitable source of heat, connected to receiver I 8, 28 are inlet and outlet conduits for heat exchanger I9, 2I is a thermostat in receiver I 8, 22 is a fuel regulating valve actuated by thermostat 2I, 23 is a vent from receiver I8 to atmosphere, 24 is a heat exchanger, is a conduit between valve I8 and evaporator 8, 26 is a conduit between valve I6 and heat exchanger 24, 21 is a steam actuated vjet pump which is functionally similar in all figures where itis shown, 28 is a conduit between heat exchanger 24 and receiver I 8, 29 is a Venturi nozzle in jet pump 21, 3B is a Venturi diffuser in jet pump 21, 3I is a throat in jet pump 21, 32 is a mixing chamber in jet pump 21, 33 is a valve, 34 is a float actuating valve 33, 35 is a conduit between heat exchanger 24 and valve 33, 38 is a conduit between valve 33 and receiver I8, 31 is a steam compressor, 38 is a motor driving compressor 31. Applying only to Figure 3, 39 is a pump, 40 is a partition, 4I is a conduit, 42 are spray nozzles, 43 is a conduit, 44 is a thermostatically controlled valve, 45 is a thermostat controlling valve 44. 46 is a suction conduit applicable only to Figures 5 and 6. Applying to all arrangements 41 is a discharge conduit from compressor 31 to jet pump 21, 48 is a conduit from evaporator B to pump I2, 49 is insulation on receiver I8 and connecting conduits, 50 is insulation on evaporator 8 and connecting conduits. Applying only to Figures 1 and 5, 5I are cooling fins on diffuser of jet pump 21. 52 in Figure 5 is an internally finned heat transfer surface from jet pump 21 to steam space 53. 53 in Figures l, 3 and 5 is a steam space in receiver I8, 54 are internal fins on part 52, 55 is internal iin heat transfer surface between jet pump 21 and compressor 31 in Figure 1 only, 56 are internal fins to part 55, shown in Figure 2 only, 51 is collecting header from parts 55 applying to Figures 1 and 2 only, 58 is connecting conduit from part 51 to compressor 31, applying to Figures 1 and 2 only, 59 is a distributing hood in Figure 1 only, 60 in Figures 8 and 9 are conduits supplying jet pump 21, 6I is a steam space in jet pump 21, 62 is a throat in Venturi nozzle 29 and jet pump 21, 93 is stream line insulation around conduit 80, 64 is insulation around jet -nozsie ti, o5 is a source the system such city water, is Water space in receiver il is a liquid level in receiver it, in i .is a conduit from coinpressor il to hood are vent holes in hood 5t, l@ in Figure 8 is an entrance opening to jet pump 2l", ll is an exit opening to jet pump t?, i2 is a conduit of small size applying to Figure 3 only, i3 is a temperature regulated valve alol plying to Figure 3 only, ld is a conduit, "itl is a water spray nozzle applying to Figures 3 and 8 only, l@ in Figure 3 is a feather weight nonn return or check valve, lli is a division line loetween aroclor and water, 'lu is a space lled with l5 aroclor. l@ is a conduit from pump 3g to water space 56, t@ in Figure 3 is suction inlet of compressor 3l, Si is a thermostat controlling Valve l.

in operation, receiver lil is lled with water from source of Water' via heat exchanger conduit 35, valve 3S, controlled by float and via conduit 3e. Heat is applied to heat exchanger is loy gas' or other heating means until sucient of this water is l eats-d and vaporized to reach a temperatme ui receiver o approximately 21:93

25 degrees at which ce thermostat 2i actuating valve 22 controls the fuel supply and maintains this temperature. When system is in cuela will hereinafter te ex- @rated in Figure l,

or from motor ie f yacuuxcation of evaporator l interconnecting transfer fers the pressure in. evapo= r conduits ill, iii and snp f `get o 2l, etc. and permits the "y of pre neatly generated oy action. of

@ heat exchanger iii as heretofore explained tico-ugh conduit and conduit tl?, steam space "us steam passing through.

nozzle 2@ and out through throat d l and heat transfer' surface is recoins-Veeco by compressor 3l at the saine time entraining with it any gases in evaporator and further yaouuniizing evaporator appiu'tenances. when pump i2 is started by means of motor it, Water will circulate through. spray ll in evaporator l and will loe cooled by evaporation to a low temperature. if evaporator E is 291/2" o vacuum or 1/2 Hg absolute pressure, its temperance wiii be approximately 59 degrees F. The steam emitted by said vagarization is pumped by jet pump 3l in the manner hereinbeiore described and is further compressed by compressor 3l after which it passes via conduit @Sito distributing hood Where a portion 6@ of it leaves through vent holes @t into steam space ci receivei i@ and goes to the atmosphare through vent 223 and the remaining portion passes through conduit l? to jet pump 2l and continues to operate said jet pump.

in normal operation a portion of the heat o compression passes from diffuser 3@ Via iins til and through heat transfer surface and tins et to Water in space et, keeping this water at the boiling temperature, approximately 212 clegrecs, and vaporizing some portion of it. Under these conditions thermostat 2l acting through control Valve 22 cuts all the fuel off of heat exchanger i9 except for a pilot light. It is thus seen that the use of fuel by heat exchanger i@ is conned to starting and standing periods.

iloe operation ir lied let pumps is weil know.L in the art t se pumps can designed under favorable conditions for high efiin ciencias. .in the design of these pumps, the dcsign of Venturi nozzle 29 and throat 62, the pitch s of the Venturi nozzle and their relation in length with themselves and with each other are well known in the art on account of the vast experience in turbine nozzle design and the efilciency can be calculated to a high degree of accuracy i0 and this portion of the device can oe designed with high efficiency. The same may be said of throat 3i and diffuser 39. One of the sources of inefficiency of` jet pumps has been the handling in the mixing space 32 of two dierent kinds of l5 elastic iiuids, usually steam as an impelling iluid and air as the uid to be pumped, or in some cases steam as an impelling fluid and steam-air mixtures as the fluid to he pumped. This has been largely eliminated in my device by prede- 20 aerating the steam supply to the jet pumps by the heating or" Water in space 65 and the venting of the emitted entrained gases through vent 23 and therefore it is possible to design jet pumps :for this service with somewhat higher eiciencies 25 thee-i has heretofore been the case.

a further source of ineiiciency has been tite admxtuie o5 an impelling iiuio as steam with the l. to or air, c

l entirely different characteristics such 3@ as the Vyture of steam emitted from Venturi nozzle suoerheateci or with large percentage i 1noistur^ space with saturated steam at the corresponding pressure. it is generally conceded tiio.- o the rnost perfect mixtures and therefore the high.-

two iuids oi the same characteistics or ii' the characteristics must be different, with a moderate degree oi supersaturation in the case of the 4@ injoei'ung (steam).

'in system, it is possible by properly coor dinating steeun compressor the amount of heat transfer surface de, and other design features provide pressures and temperatures oi steam entering jet nozzle t2 which will allow expansion of steam. in 'Venturi nozzle E@ entering the mixing space Si with the quality and character designed to give the inaximiun eciency. The low pressure steam entering the steam jet 50 pump l at entrance "it, pamicuarly when dealing with large volumes as will oe the case with. high vacuums, should enter directly and with as little loss as possible due to turns or swirls. has loeen provided for the design of my jet 55 pump 2l and steam conduit t@ has been insulated not only to prevent heat loss and the consequent expansion and change in quality of the vapor to loe compressed, lout also in a stream line form to allow these conduits to interfere only to the minimum degree with the ow o* vapors to ce compressed. it is therefore seen that the coordinated arrangements of my de vice between steam compressors and jet pumps and heating surface distribution permits a steam n jet pump design of an eiciency which has heretofore been impractical.

'in the operation of jet pumps, the compression is generally adiabatic or nearly so and when com- 7@ pressing saturated steam from approximately 1/2" Hg absolute to e Hg absolute, which would be a reasonable duty for the jet pump in Figure l, the temperature of the compressed steam would be slightly over 49o degrees with reasonable olii 75 i combined jet pump and compressor will be much improved because of the reduction in volumes entailed by the reduction in temperature. 'Ihis is the purpose of this surface and the compression tends to depart from the adiabatic a slight way toward the isothermal. Compressor 31 and a portion of conduit 66 are also submerged for the same purpose, all of which has a benecial eiect on the emciency of the refrigerating system as a whole, compressor 31 having a working duty in the illustration I have chosen in Figure 1 of from 4 I-Ig absolute to 30" Hg absolute pressure of 14.7# absolute.

In the other figures, the duty of the jet pumps and compressors are different from the one just discussed as will hereinafter be explained.

As the water continues to evaporate in evaporator 5, it must be replenished and provision is made to do this via conduit 28, heat exchanger 26, regulating valve i6 and conduit 25. Water is taken from water space 66 by this arrangement and is therefore water which has been heated and consequently deaerated. Such water entering evaporator 8 is cooled by heat exchanger 25 by the incoming water used to replace it and is desirable for use in evaporator il because it will not emit any appreciable quantity or'l noncondensable gases when vaporized.

The heat exchange surface ns 56 are installed for the purpose of increasing the heat transfer on heat exchange surface 55 to thereby improve the overall efficiency of the apparatus.

The air transferred by fans l from louvers 5 over radiating surface li of heat exchanger 3 is cooled by the removal of its heat and the absorption of said heat in heat exchanger 3 and is in some cases dehumidified by the reduction of temperature below the dew point of the air.

In Figure 3, the operation is similar to that of Figure 1 but different in some respects. In this case. jet pump 21 has a duty from 1/2" Hg absolute pressure to atmosphere or 30" Hg absolute pressure and the compressor 31 takes steam vla inlet 56 at the pressure and temperature of the discharge of jet pump 21 and therefore compresses it to a point where it can act as an impelling fluid for said jet pump. For the purpose of illustration, we will assume this compression to be up to absolute. Steam then passes through conduit 41 to Iiet pump 21 as before and performs the vacuumizing duty on evaporator 8 in a similar manner as previously described. Pump 39 takes water from water space 66 via conduit 19 and sprays a large portion of it via conduit 4l and through sprays 42, this serving to produce very good deaeration of the water and to remove in a thorough manner all entrained gases. l minor portion of this water passes through conduit 43, valve 44, to the suction of compressor 31. The compression of steam by compressors follow in general along adiabatic lines and the temperature would go quite high with a corresponding consumption of power without cooling. In order to match the temperatures most advantageous for the operation of jet pump 21, to properly cool compressor 31 and to improve the efficiency of compressor 31, water is introduced in the suction of this compressor as heretofore explained. In a similar manner, in compressing steam from l/y Hg absolute pressure to 30" Hg absolute pressure in jet pump `21 of Figure 3 very high temperatures would be produced particularly with compressing.

the range of pressure involved and considerable power would be used in producing these high temperatures. To decrease this power and to improve the efficiency of jet pump 21, I have introduced water via conduit 12, valve 13, conduit 1B and nozzle 15 into mixing chamber 32 of jet pump 21. This water is vaporized by the heat herelnbefore mentioned and in so doing reduces the net power or work required for the operation4 of jet pump 21 and also reduces the amount of 10 described, it is assumed for the purpose of illus- 15 tration, that jet pumps can be constructed with 100% efciency. In that case, with steam entering jet pump 21 at 1/2" Hg absolute pressure as in Figure 3, in a dry saturated condition and being compressed to atmospheric pressure or 30 Hg. absolute by adiabatic compressionv (constant entropy), the energy required for this compression will be approximately 460 B. t. u. ard the resultant final temperature would be in the neighborhood of 900 degrees F. of energy of the aforesaid 400 B. t. u. there would be compressed 1 pound of steam from the vaporization of lvpound of water to vapor at 1/" Hg absolute to 30 Hg absoluter The latent heat of vaporization at Mg" Hg is approximately 1059 nozzle 15, .165# of water mixed with .835# of water vapor, the energy required to compress this mixture from 1/2" Hg to 30" Hg on the same basis would be approximately 240.5 B. t. u. rEhe heat absorption in the evaporator per pound of this mixture would be 1059 .835=844.26 which divided by 240 gives a ratio of B. t. u. required for energy for compression as against B. t. u. absorbed in the evaporator per pound of 3.61 to l, a considerable gain as compared with the previous example without cooling of 2.64 to 1. The eiciencies of the jet pumps in the two cases would be similar and therefore the above gives a reasonably true indication of the magnitude of the saving to be accomplished by this arrangement. Inasmuch as the energy for actuating the jet pump all comes from compressor 31 in the form of power, this is directly reflected in the power consumption of the refrigerating device.

Partition 40 allows an adjustment of temperatures between exhaust of jet pump 21 and intake of compressor 31 and the water distribution in the pump and compressor in the most advantageous manner.

In Figure 5, jet pump 21 has a similar duty to that in Figure 3 and compresses steam from evaporator 8 to receiver I8 with a duty of approximately from 1/2 Hg absolute to 30" Hg absolute pressures. The heat of compression in this case is absorbed by water in space 65 by means of ns 5I and heatv absorbing surface 52 and fins 54 therein. Compressor 31 works in the same manner as in the previous case with the exception that it is submerged for its cooling effect and does not have water actually mixed with the steam it is proper distribution of heat exchange surfaces can be greatly similar to the results obtained with the arrangement in Figure 3. O

In accordance with drawing, Figure 3, I have For the expenditure The results obtained with the -0 shown a means to provide a cooling and lubricating duid around compressor 31. For tliis fluid I prefer aroclor (chlorinated diphenyl), a high.

boiling point hydro-carbon heavier than water and non-miscible therewith, an excellent lubricant, a good conductor of heat and a good electrical insulator. The submerglng of compressor 31 in this uid prevents corrosion of the iron and steel parts, permits the pumps to be 'built with proper lubricating openings and permits the aroclor to lubricate these pumps via such openings. In cases where driving motor is located internal to the device, is also submerged in aroclor and the aroclor acts as an insulating iiuid for the same. The material being heavier than water will stay in the position indicated and Iany portion passing through the compressor will return to the said position. 'I'he high boiling point of the substance prevents its escape by vaporization and therefore little, if any, of this substance is lost.

The heated surfaces of these devices are insulated with materiai'suitable for withstanding heat and the cooled surfaces are insulated with material suitable for this purpose.

While I have shown and described one embodiment of my invention in accordance with the patent statutes, and have shown the important modifications thereto, and explained in detail the function of the various parts of the apparatus so that one skilled in the art can understand the apparatus, it is understood that my invention is capableof embodiment in a variety of forms of apparatus and I am not limited to the specic form of arrangement or structural parts shown and described but that the scope of my invention is to be gauged by the accompanying claims taken in connection with prior art.

I claim:

1. In a water refrigeration system, an evaporator inheat transfer relation with a iluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited to actuating fluid only, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, venting means for said receiver, liquid supply means to said evaporator.

2. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited toactuating iiuid only, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, heat exchange means between water in said receiver and vapors compressed by said vacuumizing means, venting means for said receiver, liquid supply means to said evaporator.

3. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, Water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited toA actuating iiuid only, heat exchange means between vapor compressed by said compressing means and water in said receiver, vapor pressure actuated jet pumping and vacuumizing means between said evaporatorand said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, venting means for said receiver, liquid supply means to said evaporator.

4. In a water refrigeration system, an evaporator in heat transfer relation with a iluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited to actuating uid only, heat exchange means between vapor compressed by said compressor and water in said receiver, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, heat exchange means between water in said receiver and vapors compressed by said vacuumizing means, venting means for said receiver, liquid water in said evaporator, vaporizing means for water in said receiver, thermostatic control means for said vaporizing means, vapor compressing means limited to actuating fluid only, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, heat exchange means between water in said receiver and vapors compressed by said vacuumizing means, venting means for said receiver, liquid supply means to said evaporator.

6. In a water refrigeration system, an evaporator in heat transfer relation with a iluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited to actuatmgfluid only, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, cooling means cooling vapors u uniizing means, venting means for said receiver liquid supply means to said evaporator.

l7. In a water refrigeration system, an e'v'aporatorr in heat transfer relation with a. iiuid to be cooled, a receiver, water disposed said evaporator and said receiver, vaporizing means for compressed by said vacwater, vapor compressing means limited to actuating iluid only, cooling means for cooling vapors compressed by said compressing means, vapor means between said evaporator and said re' ceiver, said jet pumping and vacuumizing means being -in actuating relation with said vapor compressing means, venting means for said receiver, liquid supply means to said evaporator.

8. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporlzing means for water, vapor compressing means limited to actuy ating fluid only, cooling means for vapor compressed by said compressing means, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, y

said jet pumping and vacuumizing means being in A `actuating relation with said vapor compressing 55 pressure actuated .iet pumping and vacuumizing k l said receiver, liquid supply means to said evaporator.

9. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited to actuating fluid only, liquid injection cooling means in said compressing means, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means venting means from said receiver, liquid supply means to said evaporator.

10. In a water refrigeration system, an evaporator in heat transfer relation with a iiuid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited to actuating fluid only, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, liquid injection cooling means in said vacuumizing means, venting means for said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, liquid supply means to said evaporator.

11. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water, vapor compressing means limited to actuating uid only, liquid injection cooling means for said compressor, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, liquid injection cooling means in said vacuumizing means, venting means from said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, liquid supply means to said evaporator.

12. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporlzing means for e Lier, vapor compressing means limited to actuating uid only, liquid injection cooling means in said compressing means, thermostatic means controlling said liquid, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, venting means for said receiver, liquid supply means to said evaporator.

13. In a. water refrigeration system, an evaporator in heat transfer relation with a uid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water in said vaporator, vaporizing means for water in said receiver, vapor compressing means limited to actuating uid only, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, liquid injection cooling means in said vacuumizing means, thermostatic means controlling said liquid, venting means for said receiver, liquid supply means to said evaporator.

14. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for water in said evaporator, vaporizing means for water in said receiver, vapor compressing means limited to actuating fluid only, liquid injection cooling means for said compressor, thermostatic means controlling said liquid, vapor pressure actuated jet pumping and vacuumzing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, liquid injection cooling means in said vacuumizing means, thermostatic means controlling said liquid, venting means for said receiver, liquid supply means to said evaporator.

15. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for said water, deaerating means for said water, vapor compressing means limited to actuating fluid only, vapor pressure actuated.jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, venting means for said receiver, liquid supply means to said evaporator.

16. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver at predetermined levels, vaporizing means for said water, vapor compressing means limited to actuating fluid only, vapor pressure actuated jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor cornpressing means, level regulated liquid supply means to said receiver, level regulated liquid supply means from said receiver to said evaporator, venting means for said receiver.

17. In a water refrigeration system, an evaporator in heat transfer relation with a fluid to be cooled, a receiver, water disposed in said evaporator and said receiver, vaporizing means for said water, vapor compressing means limited to actuating fluid only, vapor pressure jet pumping and vacuumizing means between said evaporator and said receiver, said jet pumping and vacuumizing means being in actuating relation with said vapor compressing means, venting means for said receiver, liquid supply means to said receiver, liquid supply means from said receiver to said evaporator, heat exchange means between the said two liquid supply means.

RALPH C. ROE. 

